Abstract: A hydrant coupling assembly includes a hydrant valve and a hydrant coupler, including a coupler body and a coupler actuating collar assembly having an actuating collar movable axially relative to the coupler body. The actuating collar includes at least one movable latching lug that is selectively moved into place around a mating feature on the hydrant valve adapter by lifting or lowering the actuating collar. A locking mechanism is installed within the coupler actuating collar and includes a coupler plunger, a collar plunger, a coupler plunger check ball, and a collar plunger cheek ball. The coupler plunger and the coupler plunger check ball are adapted to lock the actuating collar in a disconnected state and the collar plunger and the collar plunger check ball are adapted to lock the actuating collar in a connected state. A hydrant coupler for use in a hydrant coupling assembly is also disclosed.

Abstract: A radial pump has a housing with a cylinder ring is pivotally mounted therein. The cylinder ring has a circular aperture within which a cam surface is formed. A cylinder block rotates within the cylinder ring aperture and has a plurality of radially extending cylinders each having port which selectively communicates with a fluid inlet and a fluid outlet as the cylinder block rotates. A plurality of pistons is slideably received within the cylinders and engages the cam surface. An actuator operably coupled to produce movement of the cylinder ring, which alters the spatial relationship between the cylinder ring and the cylinder block to vary the amount that the pistons move within the cylinders. The amount of movement of the pistons within the cylinders is directly related to the magnitude of fluid flow delivered by the pump and moving the cylinder ring thereby controls the fluid flow.

Abstract: A flow regulator includes a body with an aperture into which an inlet and an outlet open. A pin has a bore extending therein and communicating with the outlet. A first aperture, a second aperture and a bypass orifice are spaced longitudinally along the pin and extend there through opening into the bore. A valve member is slideably located around the pin and is biased by a spring into a first position along the pin in which the valve member closes the first aperture while opening the second aperture. When a pressure differential between the inlet and outlet exceeds a first level, the valve member moves away from the first position and begins covering the second aperture. Thereafter continuing increase of the pressure differential above a greater second level results in the valve member moving into a second position at which both the first and second apertures are closed. However in the second position, a secondary flow path exists between the inlet and the outlet through the bypass orifice.

Abstract: A valve control system (15) in which there is provided a deactivating rocker arm (51) disposed beneath a conventional, upper rocker arm (27), and disposed within a module housing (17). The deactivating rocker arm includes a latch tab (63) and when the latch tab engages (FIG. 3) a latch member (65), the system operates in a normal, valve activating mode. When the latch member is in an unlatched condition (FIG. 4), the deactivating rocker arm pivots, compressing the valve return spring (41), which thereafter serves as the required lost motion spring, biasing the deactivating rocker arm (51) and lash compensation device (35) back toward their normal position.

Abstract: A differential gear mechanism (11) and improved axle shaft (53) retention arrangement for the axle shaft. The mechanism includes a side gear (27) defining first internal splines, a coupling (35) defining second internal splines (35S), and a rotor (49) of a gerotor pump defining third internal splines (49S). The axle shaft includes external splines (55), an annular groove (57), and a collapsible and expandable retention ring (59) within the groove. The assembly operator aligns the external splines with the third internal splines (49S), then with the second internal splines (35S), and finally, with the first internal splines (27S), before exerting force (“F” in FIG. 3) on the axle shaft to collapse the retention ring by passing it through the third internal splines (49S) until the ring can expand (FIG. 4). The axle shaft is retained as the retention ring engages an inboard end (69) of the third internal splines.